DE102007048328B4 - Constant velocity fixed joint - Google Patents

Abstract

Constant velocity fixed joint, comprising an outer joint part (2) which has a cage guide surface (7) and a plurality of ball running grooves (9) on its inner circumference, an inner joint part (3) which has a cage guide surface (8) and a large number of ball running grooves (10) on its outer circumference. has a cage (4) arranged between the outer joint part (2) and the inner joint part (3), which is guided between the cage guide surfaces (7, 8) of the outer joint part (2) and the inner joint part (3), and balls (6) which are each arranged in a window (5) of the cage (4) and are held by this in a joint center plane (E) and are in engagement with the ball grooves (9, 10) of the joint outer part (2) and the joint inner part (3) for torque transmission, characterized in that, when the joint is extended, three lubricant gaps (S1, S2, SM) are formed between a cage guide surface (7, 8) and the associated counter surface (12, 13) of the cage (4), which are tapered by locally Radial distances between the cage guide surface (7, 8) and the mating surface (12, 13) of the cage (4) are delimited from one another in the axial direction of the joint, a central lubricant gap (SM) being arranged between two lateral lubricant gaps (S1, S2) which each taper in the direction of the central lubricant gap (SM), and the central lubricant gap (SM) is sickle-shaped and tapers continuously towards its two axial ends.

Description

The invention relates to a constant velocity fixed joint according to the preamble of patent claim 1.

Such fixed constant velocity joints are used, among other things, in cardan shafts of motor vehicles in order to enable torque transmission with angular compensation. In front-wheel drive vehicles, a constant velocity fixed joint is usually provided on the wheel side, while a sliding joint, for example a spherical sliding joint or a tripod sliding joint, is arranged on the gear side, which in addition to angular compensation also enables axial compensation.

In operation, especially when the joint is flexed, there are losses in terms of the transmitted power, which are noticeable in a motor vehicle through a tendency towards increased fuel consumption and increased CO ₂ emissions.

The power losses, which are mainly due to friction, also lead to the joint heating up, which can damage the joint with a very high power throughput and low heat dissipation.

With normal installation positions, conventional cardan shafts have an efficiency of around 99% to 99.5%. On the cardan shafts used as side shafts on motor vehicles, the greatest power loss is generally due to the constant velocity fixed joint.

Based on this, the invention is based on the object of creating a constant velocity fixed joint with lower friction losses.

On fixed joints of the type mentioned at the outset, internal axial forces between the outer joint part and the cage and between the inner joint part and the cage cause friction. Studies show that around 80% of the friction occurs on the cage guide surfaces, although they are not directly involved in torque transmission.

In conventional constant velocity fixed joints, the cage guide surfaces are often designed as spherical surfaces. In further embodiments, only the axial end areas are spherical, while the areas in between deviate slightly from the spherical shape, so that there are gaps between the cage and the outer joint part or inner joint part and contact in the area of self-locking is avoided.

From Seherr-Thoss, Schmelz, Auktor: Joints and joint shafts, ISBN 3-540-41759-1, it is also known to provide a radius of curvature on the outer circumference of the cage that is consistently greater than the distance from the center of the joint flexion. In the same way, the radius of curvature on the inner circumference of the cage is continuously reduced compared to the distance from the center of flexion of the joint. In cooperation with spherical ball guide surfaces on the outer joint part and on the inner joint part, sickle-shaped gaps are thus produced between the individual components.

One according to the preamble of claim 1 is off US 6,280,337 B1 known. This has a load-bearing conical ramp section on the outer joint part for guiding the cage, to which a recess adjoins. Likewise, the cage has a load-bearing, conical ramp section on its inner circumference for support against the inner joint part. A recess also adjoins this conical ramp section. The recesses serve to improve the lubrication of the joint.

Further constant velocity fixed joints are off DE 103 12 880 A1 and DE 103 29 230 A1 known.

The above-mentioned object is achieved by a joint according to patent claim 1.

This improves the supply of lubricant to the closest contact points between the cage and the associated cage guide surfaces of the outer joint part and the inner joint part, since this can now take place from both sides. This reduces the friction in the joint and leads to an improvement in efficiency. Due to the additional lateral lubricant gap, however, the middle lubricant gap in the axial direction of the joint is significantly shorter than in conventional solutions.

The ratio of the angular range of a lateral gap to the angular range of the middle gap based on the center of curvature of the associated pair of surfaces is preferably in the range from 0.3 to 0.7.

In an advantageous embodiment, the angular range of a lateral lubricant gap in relation to the center of curvature of the associated pair of surfaces is at least 9 ° and is preferably in the range from 9 to 25 °.

The lubricant gaps are generated by deviations of the cage guide surfaces and / or the associated counter surfaces of the cage from an exact spherical shape. For example, a cage guide surface or counter surface can have corresponding deviations are manufactured, while the associated counter surface or cage guide surface is manufactured without deviations from a spherical shape.

According to an advantageous embodiment, the lubricant gaps between the inner joint part and the cage are generated by deviations of the inner surface of the cage from a spherical shape, while the cage guide surface on the inner joint part has a spherical shape. The lubricant gaps are generated between the outer joint part and the cage by deviations of the cage guide surface on the outer joint part from a spherical shape, while the outer surface of the cage has a spherical shape. This avoids excessive restriction of the thickness of the cage in the area of the windows for the raceway balls.

Such a lubricant gap configuration can be implemented with relatively little effort in that the cage guide surface on the inner joint part has a constant radius R _I around a center of curvature P _I has on the longitudinal center axis of the inner joint part and the associated inner surface on the cage in the area of the lateral lubricant gaps has a radius R _Ki1 which is 1.05 to 1.2 times R _i , and a radius in the area of the central lubricant gap R _KiM , which is 0.4 to 0.7 times Ri. The sections with different radii on the cage merge tangentially into one another.

Accordingly, it can be provided for the cage guide on the outer joint part that the outside of the cage has a constant radius R _Ka around a center of curvature P _Ka having on the longitudinal center axis of the cage. The associated cage guide surface on the outer joint part has a radius in the area of the lateral lubricant gaps R _A1 which is 1.05 to 1.2 times of R _Ka and a radius in the area of the central lubricant gap R _AM that is 0.4 to 0.7 times the R _Ka is, the sections with different radii merge tangentially into one another on the cage guide surface.

A further improvement in efficiency can be achieved via the actual contact surfaces between the cage and the cage guide surfaces. In all known designs, the outer joint part, the inner joint part and the cage are supported on one another via surface sections extending in a ring around the entire circumference of the components. When the joint is rotated and flexed at the same time, the greatest frictional losses occur on those contact surfaces where there is a large relative movement between the outer joint part and the cage and the inner joint part and the cage. These contact surfaces include locations with a relatively large distance from the flexion axis.

In contrast to this, support is only provided on locally restricted, non-circumferential sections near the flexion axis of the joint, so that lower friction losses occur on the actual contact surfaces compared to conventional joints. For each pair of components there are only two opposing, local contact surfaces which, in contrast to conventional joints, are not circumferential.

This is made possible by a constant velocity fixed joint of the type mentioned at the outset, in which the cage guide surface of the outer joint part has a contact area for bearing against a contact area of an outer surface of the cage, the radius of curvature R _A of the contact area on the outer joint part is greater than its distance A _A the flexion center of the joint and the radius of curvature R _KA of the contact area on the outer surface of the cage is smaller than its distance AKA from the center of flexion of the joint and / or the cage guide surface of the inner joint part has a contact area for contact with a contact area of an inner surface of the cage, the radius of curvature R _I of the contact area on the inner joint part is smaller than its distance A _I to the flexion center of the joint, and the radius of curvature R _KI of the contact area on the inner surface of the cage is greater than its distance A _AI to the flexion center of the joint.

Since the actual contact surfaces between the outer joint part or inner joint part and the cage are limited to precisely definable, delimited areas, namely the aforementioned contact areas, narrow manufacturing tolerances only need to be adhered to in these areas. The remaining sections of the cage guide surfaces and the outer and inner surfaces on the cage can be produced with larger tolerances, which has a positive effect on the production costs.

In an advantageous embodiment, hard machining can be dispensed with outside the contact areas.

Furthermore, the contact areas can be used to measure the components and to control the dimensions of the production, which improves reproducibility and accuracy.

Since when the joint is flexed, the actual contact surfaces on the respective components are circumferential, thus alternating phases of contact with phases of spacing at the contact areas, lubricant can penetrate into the temporarily formed gaps during one cycle in order to create friction during subsequent contact minimize. In contrast to this, in the conventional embodiments explained at the outset, the lubricant supply is often unfavorable at high loads due to the relatively large actual contact surfaces and the permanent contact.

The principle according to the invention is suitable for all joint designs in which the joint components are guided axially. It is fundamentally independent of the number of balls, which can be 6, 7 or 8, for example, and of the orientation of the opening angle of the pairs of ball grooves.

For example, all pairs of ball raceways can open in the same direction, with the contact areas on the outer joint part and on the outer surface of the cage on the opening side and the contact area on the inner joint part and on the inner surface of the cage being arranged opposite the opening side.

In so-called counter-track joints, in which different pairs of ball raceways open in the circumferential direction, for example alternately in opposite directions, the contact areas on the outer joint part, the inner joint part and the inner and outer surfaces of the cage are provided on both sides of the joint center plane of the non-flexed joint.

Without being restricted to the latter type of joint, a symmetrical design of the ball cage can be advantageous.

Further, advantageous embodiments of the invention are specified in the patent claims.

The contact area of the cage guide surface on the outer joint part, when the joint is not flexed, is preferably in an angular range of 8 ° to 25 ° and more preferably 13 ° to 20 ° to the joint center plane.

For the corresponding contact area on the outer surface of the cage, an angular range of 8 ° to 25 °, preferably 13 ° to 20 °, to the joint center plane has proven to be particularly advantageous.

According to a further advantageous embodiment of the invention, the center of curvature of the contact area of the cage guide surface on the outer joint part and / or the contact area on the outer surface of the cage is offset both axially and radially with respect to the joint flexion center.

The distance is preferably at the contact area of the outer joint part A _A from the joint flexion center to the radius of curvature R _A in the ratio of 1.001 < R _A / A _A <3.

The distance A _K from the joint flexion center to the radius of curvature is at the contact area of the outer surface of the cage R _KA in the ratio of 1.001 < A _KA / R _KA <1.7.

The larger this ratio is chosen, the smaller the actual contact areas. The ratio is thus limited upwards by the maximum surface pressures that can be permitted taking into account wear and material fatigue.

In order to limit the actual contact surfaces when the joint is bent to defined, local areas, a further advantageous embodiment of the invention provides that a section with a smaller radius of curvature adjoins the contact area of the cage guide surface on the inner circumference of the outer joint part. The latter preferably extends over a central plane of the joint E. at the non-flexed joint enclosing area.

On the outer joint part, the section with a smaller radius of curvature can be followed by a further section whose radius of curvature is greater than its distance from the center of flexion of the joint.

In particular in the case of a counter track joint, this further section can be designed symmetrically to the contact area and take on a corresponding function. However, it is also possible that the radius of curvature of the further section is smaller than the radius of curvature of the contact area.

Corresponding to the outer joint part, a section with a larger radius of curvature can adjoin the contact area of the outer surface of the cage in order to limit the actual contact surfaces.

According to a further advantageous embodiment, the section with a larger radius of curvature on the outer surface of the cage is followed by a further section, the radius of curvature of which is smaller than its distance from the joint flexion center, whereby self-locking can be avoided in cooperation with the outer joint part.

In the case of a joint whose ball raceway pairs all open in the same direction, the radius of curvature of the further section can be made larger than the radius of curvature of the contact area on the outer surface of the cage. At On the other hand, a design that is symmetrical to the contact area is recommended. Furthermore, the ball grooves can be crossed.

An analog configuration can be made between the inner joint part and the cage to limit the actual contact surfaces.

For the contact area of the cage guide surface on the inner joint part when the joint is not flexed, an angular range of 10 ° to 35 °, preferably 22 ° to 30 ° to the joint center plane has proven to be particularly advantageous with regard to reducing the friction losses. Correspondingly, the contact area on the inner surface of the cage is in an angular range of preferably 10 ° to 35 ° and more preferably 22 ° to 30 ° to the joint center plane.

Furthermore, as for the contact areas between the outer joint part and the cage, the center of curvature of the contact area of the cage guide surface on the inner joint part and / or the contact area on the inner surface of the cage can be axially and radially offset from the joint flexion center.

The distance is preferably at the contact area of the inner joint part A _I from the joint flexion center to the radius of curvature R _I in the ratio 1.001 <A _{I /} R _I <1.7.

The distance is preferably at the contact area of the inner surface of the cage A _AI from the joint flexion center to the radius of curvature R _KI in the ratio 1.001 <R _{KI /} A _KI <1.9.

The contact areas can be designed as pure circular arc sections or as elliptical sections with the aforementioned radii of curvature. It is also possible to approximate this by means of curves consisting of several circular arc sections, elliptical sections and / or straight lines.

• 1 eine Schnittansicht eines Gleichlaufgelenks nach einem ersten Ausführungsbeispiel der Erfindung im gebeugten Zustand,
• 2 eine Längsschnittansicht des Gelenks aus 1 zur Veranschaulichung der Führung des Käfigs am Gelenkinnenteil bei gestrecktem Gelenk,
• 3 eine Längsschnittansicht des Gelenks aus 1 zur Veranschaulichung der Führung des Käfigs am Gelenkaußenteil,
• 4 eine Längsschnittansicht eines Gleichlauffestgelenks nach einem zweiten Ausführungsbeispiel der Erfindung im gebeugten Zustand,
• 5 eine Schnittansicht des Gelenkaußenteils, des Kugelkäfigs und des Gelenkinnenteils des Gelenks nach dem zweiten Ausführungsbeispiel in Explosionsdarstellung,
• 6 eine schematische Ansicht der Käfigführungsfläche am Gelenkaußenteil des Gelenks nach dem zweiten Ausführungsbeispiel,
• 7 eine schematische Ansicht der Außenfläche des Käfigs des Gelenks nach dem zweiten Ausführungsbeispiel,
• 8 eine schematische Ansicht der Käfigführungsfläche am Gelenkinnenteil des Gelenks nach dem zweiten Ausführungsbeispiel, und in
• 9 eine schematische Ansicht der Innenfläche des Käfigs des Gelenks nach dem zweiten Ausführungsbeispiel.

The invention is illustrated in more detail below with reference to the exemplary embodiments shown in the drawing. The drawing shows in:

• 1 a sectional view of a constant velocity joint according to a first embodiment of the invention in the flexed state,
• 2 a longitudinal sectional view of the joint 1 to illustrate the guidance of the cage on the inner joint part with the joint extended,
• 3 a longitudinal sectional view of the joint 1 to illustrate the guidance of the cage on the outer joint part,
• 4th a longitudinal sectional view of a constant velocity fixed joint according to a second embodiment of the invention in the bent state,
• 5 a sectional view of the outer joint part, the ball cage and the inner joint part of the joint according to the second embodiment in an exploded view,
• 6th a schematic view of the cage guide surface on the outer joint part of the joint according to the second embodiment,
• 7th a schematic view of the outer surface of the cage of the joint according to the second embodiment,
• 8th a schematic view of the cage guide surface on the inner joint part of the joint according to the second embodiment, and in
• 9 a schematic view of the inner surface of the cage of the joint according to the second embodiment.

The exemplary embodiments each relate to a constant velocity fixed joint 1 , which can be installed, for example, in a cardan shaft for a motor vehicle in order to transmit drive power from a transmission to a vehicle front wheel. If a sliding part (not shown here) is also provided on such a device, two constant velocity fixed joints can be used on the cardan shaft. Otherwise, a constant velocity displacement joint is used at one connection end. Different bending angles are required depending on the arrangement on the wheel side or on the vehicle side. If the constant velocity fixed joint is on the gear side, flexion angles of up to 50 degrees are required in relation to a non-flexed position. The constant velocity fixed joint 1 according to the exemplary embodiment, however, sits on the wheel side and allows flexion angles of up to 52 degrees.

The ones in the 1 and 4th constant velocity fixed joints shown 1 each comprise an outer joint part 2 and an inner joint part 3 . Between the outer joint part 2 and the inner joint part 3 is a cage 4th arranged of a variety of windows 5 to hold one ball each 6th trains.

The outer joint part 2 has a cage guide surface on its inner circumference 7th as well as a variety of ball grooves 9 on. In the same way are on the outer circumference of the inner joint part 3 a cage guide surface 8th as well as a variety of ball grooves 10 intended. The cage guide surfaces 7th and 8th are curved so that the cage 4th between the inner joint part 2 and the outer joint part 3 is secured axially, but around the flexion center Z of the joint can be pivoted.

About the cage 4th become the balls 6th , each with a ball groove 9 or. 10 of the outer joint part 2 and the inner joint part 3 are in engagement for the purpose of torque transmission, held when the joint is bent in its half-angle plane. The 1 and 4th show the joint 1 in the bent position in which the component axes A. and C. of the outer joint part 2 and the inner joint part 3 a flexion angle a lock in. The component axis B. of the cage 4th is to the component axes A. and C. of the outer joint part 2 and the inner joint part 3 each angled by a / 2.

In the first exemplary embodiment, the joint is controlled on the one hand by an axial offset of the cage guide and also by an offset of the ball running grooves. As 2 shows point for guiding the cage 4th relevant surfaces centers of curvature P _Ka and P _I on that to the flexion center Z of the joint passing through the intersection of the axes A. and C. is defined, in opposite directions by an offset OFF _Ka and OFF _{I are} axially offset. In addition to the axial offset of the cage guide, the balls in the illustrated joint 6th controlled by a second control system, namely a career offset in the half-angle plane. For this purpose, the centers of curvature are the effective ball track radii of the outer joint part 2 and the inner joint part 3 axial to the center of the joint Z offset. The location of the balls 6th When the joint is bent, this results on the one hand from the intersection of the effective ball tracks on the outer joint part 2 and on the inner part of the joint 3 . Second are the balls 6th by controlling the cage 4th out in a common, so-called homokinetic plane or half-angle plane. The cage 4th centered here over its outer and inner surfaces 12 and 13th the outer joint part 2 and the inner joint part 3 each other and at the same time guides the balls 6th in the windows 5 .

With every revolution of the joint 1 the cage performs under flexion 4th a pivoting movement around the flexion angle a . The outer and inner surfaces slide 12 and 13th of the cage 4th on the cage guide surfaces 7th and 8th of the outer joint part 2 and the outer joint part 3 . Due to the small differences in diameter, the contact points between the cage 4th and the outer joint part 2 or the inner joint part 3 with conventional joints are only sparsely supplied with lubricant. To reduce cage wear, greases with solid lubricants such as MoS ₂ are therefore often used, but these have a disadvantageous effect on the overall efficiency.

To improve the supply of lubricant to the cage guide, it is therefore proposed that three separate lubricant gaps be created between a cage guide surface and the associated counter surface of the cage S ₁ , S ₂ and S _M train who, as in the 2 and 3 shown in the axial direction of the cage 4th are arranged lying next to each other. The lubricant column S ₁ , S ₂ and S _M are due to locally tapered radial distances between the cage guide surface and the associated counter surface of the cage 4th delimited from one another in the axial direction of the joint. Of course, their position shifts when the joint is flexed compared to that in the 2 and 3 shown position with the joint extended.

In the illustrated embodiment, there is a central lubricant gap S _M between two lateral lubricant gaps S ₁ and S ₂ arranged, each in the direction of the middle lubricant gap S _M rejuvenate. The middle lubricant gap S _M is sickle-shaped and tapers to its two axial ends, to which the lateral lubricant gaps S ₁ and S ₂ connect. In the illustrated embodiment, the arrangement of the lubricant gaps is symmetrical in the axial direction. However, this can be deviated from if necessary.

The lateral lubricant gaps S ₁ and S ₂ have an axial extent that is roughly in the order of magnitude of the axial extent of the central lubricant gap S _M lies.

In relation to the center of curvature P _Ka or. P _I of the respective cage guide is the angular range γ _{1 of} a lateral lubricant gap S ₁ or. S ₂ at least 9 ° and is preferably in the range from 9 to 25 °.

The ratio of the angular range γ _{1 of} a lateral gap S ₁ or. S ₂ to the angular range γ _M of the middle gap S _M ranges from 0.3 to 0.7.

Based on 2 below is one to generate three lubricant gaps S ₁ , S ₂ and S _M suitable geometry of the surface pairing between the cage guide surface 8th of the inner joint part 3 and the associated mating surface, ie the inner surface 13th of the cage 4th are explained by way of example.

The cage guide surface 8th of the inner joint part 3 is spherical and has a radius R _I on whose center of curvature P _I on the component axis C. of the inner joint part 3 lies. The center of curvature P _I is, as already indicated above, axially offset by the amount OFF _I with respect to the joint flexion center.

The inner surface 13th of the cage 4th is composed of three circular arc-shaped sections that merge tangentially into one another. There adjoin a section with a greater curvature two less strongly curved sections laterally. As 2 shows, has the inner surface in the area of the lateral lubricant _gaps S _1i and S _2i 13th of the cage 4th a radius R _Ki1 which is 1.05 to 1.2 times of R _I amounts. The associated center of curvature P _Ki1 is opposite the center of curvature relevant for the cage guide P _I on the inner part of the joint 3 axially and radially by the amount V _axKi1 and V _radKi1 offset. This offset determines the contact angle ψ _I , under which the inner joint part 3 with the cage 4th comes into contact. In the area of the central lubricant gap S _Mi , the inner surface 13th of the cage 4th a radius R _KiM which is 0.4 to 0.7 times of R _I amounts.

The lubricant gaps S _1a , S _2a and S _Ma between the outer joint part 2 and the cage 4th however, are caused by deviations in the cage guide surface 7th on the outer joint part 2 generated by a spherical shape, while the associated mating surface, ie the outer surface 12 of the cage 4th apart from the usual manufacturing tolerances, it has an exact spherical shape.

As 3 shows, has the outer surface 12 of the cage 4th a constant radius R _Ka around a center of curvature P _Ka on the longitudinal central axis B. of the cage 4th on. The associated cage guide surface 7th on the outer joint part 2 has a radius in the area of the lateral lubricant gaps S _1a and S _2a R _A1 , which is 1.05 to 1.2 times of R _Ka amounts. In the area of the central lubricant gap S _Ma , the outer surface 12 of the cage 4th a radius R _AM which is 0.4 to 0.7 times of R _Ka amounts. The corresponding arch sections of the outer surface 12 merge tangentially.

The geometry explained above results in an unnecessary weakening of the cage 4th in the area of the cage window 5 avoided. In a modification of the illustrated embodiment, it is also possible to identify deviations in the same direction on the outer surface 12 of the cage 4th as well as on the cage guide surface 8th of the inner joint part 3 form and the inner surface of the cage 13th as well as the cage guide surface 7th of the outer joint part 8th to be spherical.

Furthermore, it is possible to apply the deviations required to generate three lubricant gaps to both parts of a pair of surfaces, ie to the cage guide surface and the associated counter surface on the cage 4th to distribute. An example of such a configuration is in particular the 6th to 9 of the second exemplary embodiment, which is explained in more detail below.

The in 4th The second embodiment shown are the ball grooves 9 and 10 preferably designed in such a way that all pairs of ball grooves each consist of a ball groove 9 on the outer joint part 2 and a ball groove 10 on the inner part of the joint 3 open in the same direction, creating large angles of flexion a make it come true. This causes the balls to move when the joint is flexed 6th pushed out in a direction F from the respective pair of ball grooves. The resulting forces are passed through the cage 4th caught, in turn with its outer surface 12 as well as its inner surface 13th on the cage guide surfaces 7th and 8th of the outer joint part 2 and the inner joint part 3 supports.

With every revolution of the joint 1 the cage performs under flexion 4th a pivoting movement around the flexion angle a . The outer and inner surfaces slide 12 and 13th of the cage 4th on the cage guide surfaces 7th and 8th of the outer joint part 2 and the inner joint part 3 .

In order to reduce the resulting friction, the outer and inner surfaces are 12 and 13th of the cage 4th as well as the cage guide surfaces 7th and 8th coordinated in a special way, namely in such a way that, when the joint is flexed, only local actual contact surfaces occur, which are at a relatively small distance from the flexion axis. The flexion axis is orthogonal to the surface, that of the component axes A. , B. and C. is stretched and runs through the pivot point Z . As a result, on the one hand, the relative speeds between the surface sections sliding against one another remain low. On the other hand, there are short lever arms to the flexion axis for the frictional forces and thus a small frictional moment, which improves the efficiency for the power transmission of the joint.

For reasons of symmetry, each pair of components results in two zones in which actual contact occurs when the joint is bent. For the component pairing outer joint part / cage, this zone is in 1 designated with S1, for the component pairing inner joint part / cage, however, with S2. It also takes place between the cage 4th and the outer joint part 2 as well as the inner joint part 3 no further actual contact takes place. In order to make this possible, corresponding contact areas are formed on the components mentioned, which are manufactured with a high degree of precision and which each only extend over partial sections of the outer and inner surfaces 12 and 13th of the cage 4th and the cage guide surfaces 7th and 8th extend. In particular, these subsections lie outside the center of flexion Z extending joint median plane E. when the joint is unbent.

In the illustrated embodiment, in which all pairs of ball grooves in the same Open direction, the contact areas are on the outer joint part 2 and on the outer surface 12 of the cage 4th on the opening side. The contact areas on the inner joint part 3 and on the inner surface 13th of the cage 4th however, are arranged opposite the opening side.

2 illustrates the design of the cage guide surfaces 7th and 8th on the outer joint part 2 and on the inner part of the joint 3 as well as the corresponding outer and inner surfaces 12 and 13th of the cage 4th .

The surrounding contact area 14th the cage guide surface 7th on the outer joint part 2 If the joint is not flexed, it is in an angular range of 8 ° to 25 °, preferably 13 ° to 20 °, to the joint center plane E. . Where is the radius of curvature R _A of the contact area 14th greater than its distance A _A to the flexion center Z of the joint. This is preferably achieved in that the center of curvature M _A of the contact area 14th opposite the joint flexion center Z is axially and radially offset.

A line connecting the flexion center of the joint Z to the center of curvature M _A forms to the plane E. an angle ε , which is between 8 ° and 25 °, with optimal design between 13 ° and 20 °.

The distance A _A from the joint flexion center Z stands for the radius of curvature R _A in the ratio 1.001 <R _A / A _A <3.

3 shows, in a schematic representation not to scale, an example of the further design of the cage guide surface 7th . With the radius r0 a fictitious spherical surface is indicated as a reference variable, to which in 4th Is referred to. When the joint is not flexed, the Y-axis coincides with the joint median plane E. together, while the X-axis corresponds to the component axis.

To the contact area 14th of the outer joint part 2 with the radius of curvature R _A who is in 3 is denoted by r3 and has the center of curvature M3, closes a section 15th with a smaller radius of curvature r2. Its center of curvature M2 lies in relation to the component axis on the other side than the center of curvature M3. To the section 15th Another section closes with a smaller radius of curvature r2 16 whose radius of curvature r1 is greater than its distance from the joint flexion center Z . In the illustrated embodiment, the radius of curvature is r1 of the further section 16 smaller than the radius of curvature r3 of the contact area 14th . The corresponding center of curvature M1 is closer to the component axis than the center of curvature M3. The different radii of curvature merge tangentially at points P1 and P2.

The surrounding contact area 17th the outer surface 12 of the cage 4th who, if necessary, through the window 5 can be interrupted, if the joint is not flexed it is in an angular range of 8 to 25 °, preferably 13 ° to 20 °, to the joint center plane E. . Where is the radius of curvature R _KA of the contact area 17th smaller than its distance A _KA to the flexion center Z of the joint. This is preferably achieved in that the center of curvature M _KA of the contact area 17th opposite the joint flexion center Z is axially and radially offset.

A line connecting the flexion center of the joint Z to the center of curvature MKA forms the plane E. an angle Φ which is between 8 ° and 25 °, with an optimal design between 13 ° and 20 °.

The distance A _KA from the joint flexion center Z stands for the radius of curvature R _KA in the ratio of 1.001 < A _KA / R _KA <1.7.

It is beneficial to the angles ε and Φ to choose immediately. The relationship R _A / A _A can be equal to the ratio A _KA / R _KA to get voted. So that the cage 4th has the greatest possible material thickness, it can be advantageous to design R _A / A _A > A _KA / R _KA .

The greater the selected curvature ratios A / R, the smaller the contact areas and thus also the actual contact surfaces. During the execution, it should be noted that the actual contact surfaces should be as small as possible on the one hand, but on the other hand the surface pressures should not be too high in order to keep wear and material fatigue within limits.

4th shows in a schematic representation not to scale an example of the further design of the outer surface 12 of the cage 4th . With the radius r0, use the fictitious spherical surface as the reference variable 3 drawn. When the joint is not flexed, the Y-axis coincides with the joint median plane E. together, while the X-axis corresponds to the component axis.

To the contact area 17th with the radius of curvature R _KA who is in 4th is denoted by r3 and has the center of curvature M3, closes a section 18th with a larger radius of curvature r2. Its center of curvature M2 lies with respect to the component axis on the other side than the center of curvature M3. To the section 18th Another section closes with a larger radius of curvature r2 19th whose radius of curvature r1 is smaller than its distance from the joint flexion center Z . In the illustrated embodiment, the radius of curvature r1 of the further section is also 19th greater than the radius of curvature r3 of the contact area 17th . The corresponding center of curvature M1 is closer to the component axis than the center of curvature M3. The different radii of curvature merge tangentially into one another at points P1 and P2.

The surrounding contact area 20th the cage guide surface 8th on the inner part of the joint 3 If the joint is not flexed, it is in an angular range of 10 ° to 35 °, preferably 22 ° to 30 °, to the joint center plane E. . Where is the radius of curvature R _I of the contact area 20th smaller than its distance A _I to the flexion center Z of the joint. For this purpose, the center of curvature is preferably M _I of the contact area 20th opposite the joint flexion center Z axially and radially offset.

A line connecting the flexion center of the joint Z to the center of curvature M _I forms to the plane E. an angle X , which is between 10 ° and 35 °, with optimal design between 22 ° and 30 °.

The distance A _I from the joint flexion center Z stands for the radius of curvature R _I in the ratio 1.001 <A _I / R _I <1.7.

Like comparing the 6th and 7th shows, when the joint is extended between the outer surface 12 of the cage 4th and the cage guide surface 7th of the outer joint part 2 three lubricant gaps S _1a , S _2a and S _Ma formed by locally tapered radial distances between the cage guide surface 7th and the mating surface 12 of the cage 4th are delimited from one another in the axial direction of the joint. In the area of the middle sections 15th and 18th the outer surface 12 of the cage 4th or the cage guide surface 7th there is a mean lubricant gap S _Ma , which tapers in the axial direction. Two lateral lubricant gaps S _1a and S _2a adjoin these, which are located in the area of the outer end sections of the contact areas 14th and 17th or. 16 and 19th expand.

5 shows, in a schematic representation not to scale, an example of the further design of the cage guide surface 8th . With the radius r0 a fictitious spherical surface is indicated as a reference variable, to which in 6th Is referred to. When the joint is not flexed, the Y-axis coincides with the joint median plane E. together, while the X-axis corresponds to the component axis.

To the contact area 20th of the inner joint part 3 with the radius of curvature R _I who is in 5 is denoted by r1 and has the center of curvature M1, closes a section 21st with a larger radius of curvature r2. Its center of curvature M2 lies in relation to the component axis on the other side than the center of curvature M1. To the section 21st Another section closes with a smaller radius of curvature r2 22nd whose radius of curvature r3 is smaller than its distance from the joint flexion center Z . In the illustrated embodiment, the radius of curvature is also r3 of the further section 22nd greater than the radius of curvature r1 of the contact area 20th . The corresponding center of curvature M3 is closer to the component axis than the center of curvature M1. The different radii of curvature merge tangentially at points P1 and P2.

The surrounding contact area 23 the inner surface 13th of the cage 4th who, if necessary, through the window 5 can be interrupted, if the joint is not flexed it is in an angular range of 10 ° to 35 °, preferably 22 ° to 30 °, to the joint center plane E. . Where is the radius of curvature R _KI of the contact area 23 greater than its distance A _AI to the flexion center Z of the joint. This is preferably achieved in that the center of curvature M _KI of the contact area 23 opposite the joint flexion center Z is axially and radially offset.

A line connecting the flexion center of the joint Z to the center of curvature M _KI forms to the plane E. an angle δ , which is between 10 ° and 35 °, with optimal design between 22 ° and 30 °.

The distance A _AI from the joint flexion center Z stands for the radius of curvature R _KI in the ratio 1.001 <R _KI / A _KI <1.9.

It is beneficial to the angles X and δ to choose right away. The relationship R _I / A _I can be chosen equal to the ratio A _{KI /} R _KI . So that the cage 4th has the greatest possible material thickness, it can be advantageous to design A _{I /} R _I > R _{KI /} A _KI .

6th shows in a schematic representation not to scale an example of the further design of the outer surface 12 of the cage 4th . With the radius r0, use the fictitious spherical surface as the reference variable 5 drawn. When the joint is not flexed, the Y-axis coincides with the joint median plane E. together, while the X-axis corresponds to the component axis.

To the contact area 23 with the radius of curvature R _KI who is in 6th is denoted by r1 and has the center of curvature M1, closes a section 24 with a smaller radius of curvature r2. Its center of curvature M2 lies in relation to the component axis on the other side than the center of curvature M1. To the section 24 Another section closes with a smaller radius of curvature r1 25th whose radius of curvature r3 is greater than its distance from the joint flexion center Z . In the illustrated embodiment, the radius of curvature is also r3 of the further section 25th smaller than the radius of curvature r1 of the contact area 23 . The corresponding center of curvature M3 is closer to the component axis than the center of curvature M1. The different radii of curvature merge tangentially into one another at points P1 and P2.

A comparison of the 8th and 9 shows that in the area of the middle sections 21st and 24 a mean lubricant gap S _{Mi is} formed, which tapers in the axial direction. These border beyond the closest approach between the cage guide surface 8th and the mating surface 13th two lateral lubricant _gaps S _1i and S _2i , which are located in the area of the axially outer end sections of the contact areas 20th and 23 or. 22nd and 25th expand.

Numerous discussions are possible from the exemplary embodiment explained above. In particular, the non-loaded sections 16 , 19th , 22nd and 25th designed in such a way that this occurs when the direction of force on the balls is reversed 6th Provide local contact surfaces. This is particularly advantageous in a configuration as a counter track joint in which the pairs of ball grooves open in opposite directions and the contact areas on the outer joint part, inner joint part and the inner and outer surfaces of the cage are provided on both sides of the joint center plane of the undeflected joint. Furthermore, a symmetrical design of the cage 4th be beneficial.

Furthermore, in contrast to the illustrated embodiment, in which the central axes of the ball running grooves 9 and 10 each in one of the component central axis A. or. C. containing radial plane, also crossed ball grooves are provided. The contact areas can be designed as in the case of the counter track joints mentioned above. In the case of reciprocal crossing, the forces are canceled out, analogous to counter-path joints.

The contact areas can be designed both as circular arc sections and as elliptical sections with the specified radii of curvature. In addition, curves consisting of several circular arc sections, elliptical sections and / or straight lines are possible.

The invention has been explained in more detail on the basis of preferred exemplary embodiments. However, it is not restricted to these, but rather encompasses all the configurations defined by the patent claims.

List of reference symbols

1

Constant velocity fixed joint

2

Joint outer part

3

Inner joint part

4th

Cage

5

window

6th

Bullet

7th

Cage guide surface

8th

Cage guide surface

9

Ball groove

10

Ball groove

12

Outer surface of the cage

13

Inner surface of the cage

14th

Contact area on the ball guide surface of the outer joint part

15th

middle section of the ball guide surface of the outer joint part

16

Another section of the ball guide surface of the outer joint part

17th

Contact area on the outer surface of the cage

18th

middle section of the outer surface of the cage

19th

another section of the outer surface of the cage

20th

Contact area on the ball guide surface of the inner joint part

21st

middle section of the ball guide surface of the inner joint part

22nd

Another section of the ball guide surface of the inner joint part

23

Contact area on the inner surface of the cage

24

middle section of the inner surface of the cage

25th

another section of the inner surface of the cage

A.

Component axis of the outer joint part

B.

Component axis of the cage

C.

Component axis of the inner joint part

E.

Joint median plane

Z

Joint flexion center

A _A

Distance contact area on the ball guide surface of the outer joint part-joint flexion center

A _KA

Distance contact area on the outer surface of the cage - joint flexion center

A _AI

Distance from the contact area on the inner surface of the cage to the joint flexion center

A _I

Distance contact area on the ball guide surface of the inner joint part-joint flexion center

M _A

Center of curvature of the contact area on the ball guide surface of the outer joint part

M _KA

Center of curvature of the contact area on the outer surface of the cage

M _KI

Center of curvature of the contact area on the inner surface of the cage

M _I

Center of curvature of the contact area on the ball guide surface of the inner joint part

OFF,

axial offset of the center of curvature of the cage guide surface of the inner joint part

OFF _Ka

axial offset of the center of curvature of the outer surface of the cage

P _A1

Center of curvature of a lateral section of the cage guide surface of the outer joint part

PAM

Center of curvature of a central section of the cage guide surface of the outer joint part

P _I

Center of curvature of the cage guide surface of the inner joint part

P _Ka

Center of curvature of the outer surface of the cage

P _Ki1

Center of curvature of a lateral section of the inner surface of the cage

P _KiM

Center of curvature of the central portion of the inner surface of the cage

R _A

Radius of curvature of the contact area on the spherical guide surface of the outer joint part

R _A1

Radius of curvature of a lateral section of the cage guide surface of the outer joint part

R _AM

Radius of curvature of a central section of the cage guide surface of the outer joint part

R _Ka

Radius of curvature of the outer surface of the cage

R _KA

Radius of curvature of the contact area on the outer surface of the cage

R _Ki1

Radius of curvature of a lateral portion of the inner surface of the cage

R _KiM

Radius of curvature of the central portion of the inner surface of the cage

R _KI

Radius of curvature of the contact area on the inner surface of the cage

R _I

Radius of curvature of the contact area on the spherical guide surface of the inner joint part

R _I

Radius of curvature of the cage guide surface of the inner joint part

S ₁

lateral lubricant gap (i: inside; a: outside)

S ₂

lateral lubricant gap (i: inside; a: outside)

S _M

lateral lubricant gap (i: inside; a: outside)

V _axKi1

axial misalignment

V _radKi1

radial misalignment

V _radKiM

radial misalignment

a

Flexion angle

γ _1.2

Angular range of a lateral lubricant gap

γ _M

Angular range of a mean lubricant gap

δ

Contact area angle

ε

Contact area angle

X

Contact area angle

ψ _I

Steering angle

ϕ

Contact area angle

Claims (37)

Constant velocity fixed joint, comprising an outer joint part (2) which has a cage guide surface (7) and a plurality of ball running grooves (9) on its inner circumference, an inner joint part (3) which has a cage guide surface (8) and a large number of ball running grooves (10) on its outer circumference ), a cage (4) arranged between the outer joint part (2) and the inner joint part (3), which is guided between the cage guide surfaces (7, 8) of the outer joint part (2) and the inner joint part (3), and balls (6) which are each arranged in a window (5) of the cage (4) and held by this in a joint center plane (E) and with the ball running grooves (9, 10) of the outer joint part (2) and the inner joint part (3) are in engagement for torque transmission, characterized in that when the joint is extended between a cage guide surface (7, 8) and the associated counter surface (12, 13) of the cage (4 ) three lubricant gaps (S ₁ , S ₂ , S _M ) are formed, which are delimited from one another in the axial direction of the joint by locally tapered radial distances between the cage guide surface (7, 8) and the counter surface (12, 13) of the cage (4), wherein a central lubricant gap (S _M ) is arranged between two lateral lubricant gaps (S ₁ , S ₂ ), which taper in the direction of the central lubricant gap (S _M ), and the central lubricant gap (S _M ) is sickle-shaped and converges its two axial ends continuously tapers. Constant velocity fixed joint according to Claim 1 , characterized in that the angular range of a lateral lubricant gap (S ₁ , S ₂ ) based on the joint flexion center (Z) is at least 9 ° and is preferably in the range from 9 to 25 °. Constant velocity fixed joint according to Claim 1 or 2 , characterized in that the ratio of the angular range of a lateral gap (S ₁ , S ₂ ) to the angular range of the central gap (S _M ) based on the joint flexion center (Z) is in the range from 0.3 to 0.7. Constant velocity fixed joint according to one of the Claims 1 to 3 , characterized in that the lubricant gaps (S ₁ , S ₂ , S _M ) between a cage guide surface and the associated counter surface on the cage are generated by deviations of the counter surface of the cage from a spherical shape, while the cage guide surface has a spherical shape. Constant velocity fixed joint according to one of the Claims 1 to 4th , characterized in that the lubricant gaps (S ₁ , S ₂ , S _M ) between a cage guide surface and the associated counter surface on the cage are generated by deviations of the cage guide surface from a spherical shape, while the counter surface of the cage has a spherical shape. Constant velocity fixed joint according to one of the Claims 1 to 5 , characterized in that the lubricant gaps (S ₁ , S ₂ , S _M ) between the inner joint part (3) and the cage (4) are generated by deviations of the inner surface (13) of the cage (4) from a spherical shape, while the cage guide surface (8) on the inner joint part (3) has a spherical shape, and the lubricant gaps (S ₁ , S ₂ , S _M ) between the outer joint part (2) and the cage (4) due to deviations of the cage guide surface (7) on the outer joint part (2) from a spherical shape are generated, while the outer surface (12) of the cage (4) has a spherical shape. Constant velocity fixed joint according to one of the Claims 1 to 6th , characterized in that the cage guide surface (8) on the inner joint part (3) has a constant radius R _I around a center of curvature P _I on the longitudinal center axis of the inner joint part (3), and the associated inner surface (13) on the cage in the area of the lateral lubricant gaps ( S ₁ , S ₂ ) has a radius R _Ki1 that is 1.05 to 1.2 times that of R _I , and in the area of the middle lubricant _gap (S _M ) a radius R _KiM that is 0.4 to 0 , 7 times R _I , the sections with different radii on the cage (4) merging tangentially into one another. Constant velocity fixed joint according to one of the Claims 1 to 7th , characterized in that the outside (12) of the cage (4) has a constant radius R _Ka around a center of curvature P _Ka on the longitudinal center axis of the cage (4), and the associated cage guide surface (7) on the outer joint part (2) in the area of lateral lubricant gap (S ₁ , S ₂ ) has a radius R _A1 , which is 1.05 to 1.2 times R _Ka , and in the area of the central lubricant gap (S _M ) a radius R _AM , which is the 0, 4 to 0.7 times R _Ka , the sections with different radii merging tangentially into one another on the cage guide surface (7). Constant velocity fixed joint according to one of the Claims 1 to 3 , characterized in that the cage guide surface (7) of the outer joint part (2) has a contact area (14) for bearing against a contact area (17) of an outer surface (12) of the cage (4), the radius of curvature R _{A of} the contact area (14) on the outer joint part (2) is greater than its distance A _A to the flexion center Z of the joint, and the radius of curvature R _{KA of} the contact area (17) on the outer surface (12) of the cage (4) is smaller than its distance AKA to the flexion center (Z) of the joint, and / or the cage guide surface (8) of the inner joint part (3) has a contact area (20) for contact with a contact area (23) of an inner surface (13) of the cage (4), the radius of curvature R _{I of} the contact area (20) on the inner joint part (3 ) is smaller than its distance A _{I from} the flexion center Z of the joint, and the radius of curvature R _{KI of} the contact area (23) on the inner surface (13) of the cage (4) is greater than its distance A _{KI from} the flexion center Z of the joint. Constant velocity fixed joint according to the generic term of Claim 1 , characterized in that the cage guide surface (7) of the outer joint part (2) has a contact area (14) for bearing against a contact area (17) of an outer surface (12) of the cage (4), the radius of curvature R _{A of} the contact area (14) on the outer joint part (2) is greater than its distance A _A to the flexion center Z of the joint, and the radius of curvature R _{KA of} the contact area (17) on the outer surface (12) of the cage (4) is smaller than its distance AKA from the flexion center (Z) of the joint, and / or the cage guide surface (8) of the inner joint part (3) has a contact area (20) for resting against a contact area (23) of an inner surface (13) of the cage (4), the radius of curvature R _{I of} the contact area (20 ) on the inner joint part (3) is smaller than its distance A _{I from} the flexion center Z of the joint, and the radius of curvature R _{KI of} the contact area (23) on the inner surface (13) of the cage (4) is greater than its distance A _{KI from} the flexion center Z of the joint. Constant velocity fixed joint according to Claim 10 , characterized in that the contact area (14) of the cage guide surface (7) on the outer joint part (2) and the contact area (17) on the outer surface (12) of the cage (4) with the joint not flexed in an angular range of 8 ° to 25 °, preferably 13 ° to 20 ° to the joint center plane (E). Constant velocity fixed joint according to Claim 11 , characterized in that a connecting line from the joint flexion center Z to the center of curvature M _A to the plane E forms an angle ε, a connecting line from the joint flexion center Z to the center of curvature MKA to the plane E forms an angle ϕ, and both angles ε and ϕ are equal. Constant velocity fixed joint according to one of the Claims 10 to 12 , characterized in that the center of curvature of the contact area (14) of the cage guide surface (7) on the outer joint part (2) and / or of the contact area (17) on the outer surface (12) of the cage (14) is axially and radially offset with respect to the joint flexion center Z. . Constant velocity fixed joint according to one of the Claims 10 to 13th , characterized in that at the contact area (14) of the outer joint part (2), the distance A _A joint flexion center Z to the radius of curvature R _A or R _{A is} in the ratio 1.001 <R _A / A _A <3. Constant velocity fixed joint according to one of the Claims 10 to 14th , characterized in that at the contact area (17) of the outer surface (12) of the cage (4) the distance A _K from the articulation center Z to the radius of curvature R _{KA is} in the ratio 1.001 <A _KA / R _KA <1.7. Constant velocity fixed joint according to one of the Claims 10 to 15th , characterized in that a section (15) with a smaller radius of curvature adjoins the contact area (14) of the cage guide surface (7) on the inner circumference of the outer joint part (2). Constant velocity fixed joint according to Claim 16 , characterized in that on the outer joint part (2) on the section (15) with a smaller radius of curvature, a further section (16) connects, the radius of curvature of which is greater than its distance from the center of flexion of the joint. Constant velocity fixed joint according to Claim 17 , characterized in that on the outer joint part (2) the radius of curvature of the further section (16) is smaller than the radius of curvature of the contact area (14). Constant velocity fixed joint according to one of the Claims 10 to 18th , characterized in that a section (18) with a larger radius of curvature adjoins the contact area (17) of the outer surface (12) of the cage (4). Constant velocity fixed joint according to Claim 19 , characterized in that on the outer surface (12) of the cage (4) on the section (18) with a larger radius of curvature a further section (19) is connected, the radius of curvature of which is smaller than its distance from the center of flexion of the joint Z. Constant velocity fixed joint according to Claim 20 , characterized in that on the outer surface (12) of the cage (4) the radius of curvature of the further section (19) is greater than the radius of curvature of the contact area (17). Constant velocity fixed joint according to one of the Claims 10 to 21st , characterized in that the contact area (20) of the cage guide surface (8) on the inner joint part (3) and the contact area (23) on the inner surface (13) of the cage (4) with an unbent joint in an angular range of 10 ° to 35 °, preferably 22 ° to 30 ° to the joint center plane (E). Constant velocity fixed joint according to one of the Claims 10 to 22nd , characterized in that a connecting line from the joint flexion center Z to the center of curvature MI to the plane E forms an angle X, a connecting line from the joint flexion center Z to the center of curvature MKI to the plane E forms an angle δ, and both angles X and δ are equal. Constant velocity fixed joint according to one of the Claims 10 to 23 , characterized in that the center of curvature of the contact area (20) of the cage guide surface (8) on the inner joint part (3) and / or of the contact area (23) on the inner surface (12) of the cage (4) is offset axially and radially with respect to the joint flexion center Z. . Constant velocity fixed joint according to one of the Claims 10 to 24 , characterized in that at the contact area (20) of the inner joint part (3), the distance A _I from the joint flexion center to the radius of curvature R _{I is} in the ratio 1.001 <A _I / R _I <1.7. Constant velocity fixed joint according to one of the Claims 10 to 25th , characterized in that at the contact area (23) inner surface (13) of the cage (4) the distance A _KI from the articulation center to the radius of curvature R _{KI is} in the ratio 1.001 <R _{KI /} A _KI <1.9. Constant velocity fixed joint according to one of the Claims 10 to 26th , characterized in that a section (21) with a larger radius of curvature adjoins the contact area (20) of the cage guide surface (8) on the outer circumference of the inner joint part (3). Constant velocity fixed joint according to Claim 27 , characterized in that the inner joint part (3) is adjoined by a further section (22) with a larger radius of curvature, the radius of curvature of which is smaller than its distance from the center of flexion of the joint Z. Constant velocity fixed joint according to Claim 28 , characterized in that on the inner joint part (3) the radius of curvature of the further section (22) is greater than the radius of curvature of the contact area (20). Constant velocity fixed joint according to one of the Claims 10 to 29 , characterized in that a section (24) with a smaller radius of curvature adjoins the contact area (23) of the inner surface (13) of the cage (4). Constant velocity fixed joint according to Claim 30 , characterized in that on the inner surface (13) of the cage (4) on the section (24) with a smaller radius of curvature, a further section (25) adjoins, the radius of curvature of which is greater than its distance from the joint flexion center Z. Constant velocity fixed joint according to Claim 31 , characterized in that on the inner surface (13) of the cage (4) the radius of curvature of the further section (25) is smaller than the radius of curvature of the contact area (23). Constant velocity fixed joint according to one of the Claims 10 to 32 , characterized in that all ball groove pairs (9, 10) open in the same direction, the contact areas (14, 17) on the outer joint part (2) and on the outer surface (12) of the cage (4) on the opening side and the contact areas (20, 23) on the inner joint part (3) and on the inner surface (13) of the cage (4) are arranged opposite the opening side. Constant velocity fixed joint according to one of the Claims 10 to 32 , characterized in that the ball groove pairs (9, 10) in the circumferential direction alternately open in opposite directions and the contact areas (14, 17, 20, 23) on the outer joint part (2), inner joint part (3) and the inner and outer surfaces (12 , 13) of the cage (4) are provided on both sides of the joint center plane (E) of the non-flexed joint. Constant velocity fixed joint according to one of the Claims 1 to 32 , characterized in that its ball grooves (9, 10) are crossed. Constant velocity fixed joint according to one of the Claims 10 to 35 , characterized in that the contact areas are designed as circular arc sections, as elliptical sections or as curves consisting of several circular arc sections, elliptical sections and / or straight lines. Constant velocity fixed joint according to one of the Claims 10 to 36 , characterized in that only the contact areas (14, 17, 20, 23) are hard-machined on the cage guide surfaces (7, 8) of the outer joint part (2) and the inner joint part (3) and on the outer and inner surface of the cage (4) .

Images